Hydraulic spooling device



1968 A. w. KUMPF 3,395,893

HYDRAULIC SPOOLING DEVICE 7 Sheets-Sheet 1 Filed Nov. 30, 1966 INVENTOR.

1906a.- WAZMPA wfloiljm i/wm 1968 A. w. KUMPF 3,395,893

HYDRAULIC SPOOLING DEVICE Filed NOV. 30, 1966 7 Sheets-Sheet 2 I N VENTOR.

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TOR/YE Y5 Aug. 6, 1968 A. w. KUMPF HYDRAULIC SPOOLING DEVICE 7Sheets-Sheet 5 Filed Nov. 30, 1966 JNVENTOR. flg eusr W Aim 1 Aug. 6,1968 A. w. KUMPF ,8

HYDRAULIC SPOOLING DEVICE Filed Nov. 30, 1966 7 Sheets-Sheet 4 INVENTOR.

Aug. 6, 1968 Filed NOV. 30, 1966 A. w. KUMPF 3,395,893

HYDRAULIC SPOOLING DEVICE 7 Sheets-Sheet 5 INVENTOR.

06057 WKU/WPF TGR/VEKS Aug 1968 A. w. KUMPF 3,395,893

HYDRAULIC SPOOLING DEVICE Filed Nov. 30, 1966 7 Sheets-Sheet 7 L 44 24 JW 234 c Pi 216 "ZZZ SELECTOR PIESEL 2 5 H P aware/c mm P V DIESEL INVENTOR.

Unit d States Patent 3,395,893 HYDRAULIC SPOOLING DEVICE August'W.Kumpf, Conshohocken,-Pa., assignor to Clyde Iron Works Inc., Duluth,Minn., a corporation of Minnesota Filed Nov. 30, 1966, Ser. No. 598,0968 Claims. (Cl. 254-190) ABSTRACT OF THE DISCLOSURE A hydraulicallydriven touring winch for marine use having a specially constructedspooling device and spooling control unit. The spooling device includesa swivelly mounted rope sheave which is reciprocated relative to thewindup drum of the winch by opposed pairs of horizontally disposedhydraulic rams. The spooling control unit includes a planetary gear sethaving a rotary output employed to adjust the control valve for thehydraulic rams. The gear set operates from two rotary inputs, one ofwhich is responsive to rotation of the windup drum, and the other ofwhich is responsive to the extent of linear movement of the rope sheave.

This invention relates to windup devices of the kind having apower-driven rotating drum for winding and unwinding a rope or the likeand to spooling units for use with such wind-up devices. In particular,it relates to a winch, such as a marine towing winch, having a spoolingunit and to a control unit for the spooling unit.

It is one object of the present invention to provide a hydraulicallyoperated spooling unit for use with a heavy duty winch, the spoolingunit having an improved hydraulic drive for reciprocating a rope guiderelative to the windup drum of the winch.

It is another object of the invention to provide an improved controlmechanism for the drive system of a spooling unit, the control mechanismhaving an output means which is responsive to the rotation of the windupdrum of a winch and to the linear movement of the spooling unit in amanner to maintain proper synchronism of the spooling unit with thewindup drum.

It is another object to provide a spooling unit for a heavy duty winchhaving an improved swivel mounting for the line guiding sheave.

General description The novel features of the present invention aredescribed and illustrated as being embodied in a marine towing winch ofthe kind which in use is mounted on the after part of the main deck of atug or the like. The invention is, however, applicable to heavy dutywindup devices generally.

The winch unit, in the form illustrated, includes as its major parts arope windup drum and associated hydraulic drive, a spooling unit havinga separate hydraulic drive for guiding the rope on and oil the windupdrum, and control systems for the drum'drive and for the spooling unitdrive.

The windup drum is journalled in a frame and is driven through gearingand shatting by hydraulic motors which are mounted on the frame. Controlof the motors is obtained with a lever-actuated pilot valve whichcontrols a main motor control valve. The lever is manually operatedbetween a neutral position and up and down positions which correspond,respectively, to stop, pay out rope and haul in rope.

The after end of the winch unit is provided with a hydraulicallyoperated spooling unit having a rope sheave mounted in a fair leadswivel block. The swivel block is carried in a spooling unit cross headwhich is mounted aft Patented Aug. I 6, 1968 of the windup drum. Thecross head is mounted for linear movement along a path which is parallelto the axis of the windup drum. When the windup drum rotates, the crosshead is moved automatically by a hydraulic drive to spool the rope on oroil the drum, depending on the direction of rotation of the latter. Thehydraulic spooling drive includes two pairs of opposed hydraulic pistonsslidably carried in cylinders which are fixed to the winch unit frame.Each pair of pistons is disposed so as to engage and support the crosshead, the pairs of pistons being mounted on opposite sides of the frameso that each pair drives the cross head in only one direction. Thecylinders are supplied with pressure oil from a hydraulic pump throughpiping and a mechanically operated directional control valve.

The directional control valve for the spooling unit is lever controlledby a mechanical control unit. In operation the control unit holds thelever in a valve-open position to effect a traverse of the spoolingunit, then moves the lever to a valve-closed position to stop thespooling unit at its reversal point, and then moves the lever to anopposite valve-open position to effect a traverse of the spooling unitin an opposite direction. The specific operation of the control unit issomewhat more complex in that it is responsive to two inputs, one ofwhich is proportional to rotation of the windup drum and the second ofwhich is proportional to the linear movement of the spooling unit crosshead. These rotary inputs are transmitted to a planetary differentialgear set which converts them to movement of the valve control leverthrough a cam rotated by the gear set. The gear set comprises two sungears and two intermeshing planetary gears each of which meshes with adilferent one of the sun gears. Rotary motion of the windup drum istransmitted by gearing and shafting to a diamond lead screw. Rotation ofthe lead screw moves a cross head pawl which, through a rack, pinion andgearing, rotates the first sun gear of the differential planetary gearset. This first input tends to produce a corresponding rotation of theplanetary carrier of the gear set on which is fitted the cam for movingthe valve lever. The second rotary input is transmitted to the secondsun gear of the gear set. This input is obtained from movement of thespooling unit cross head by means of a cable which is connected at itsends to the latter and which is looped over a pair of repeat back drumsdisposed adjacent the cross head. When the cross head moves, the cablerotates the repeat back drums, and the rotary input to the sun gear istransmitted by a shaft from the axle of one of the repeat back drums.

In operation simultaneous rotation of the sun gears by their respectiveinputs during a traverse of the spooling unit holds the planetarycarrier and the cam in a given valve-open position. The construction andarrangement of the mechanical drive from the windup drum is such thatthe first input stops just before the spooling unit arrives at itsreversal point. The second input continues, because the spooling unit isstill moving, and this produces rotation of the planetary carrier andthe cam toward a valve-closed posit-ion. Closing of the valve stops thespooling unit at its reversal point, and this stops the second input,However, by this time the mechanical drive from the windup drum hasreversed and is again producing the first input although in an oppositedirection. As a result, the planetary carrier and cam move toward anopposite valve-open position. As the valve opens the spooling unitbegins to move, and this produces the second input. The combination ofboth inputs holds the carrier and cam in the valve-open position.

The invention will be further understood from the following detaileddescription taken with the drawings in which:

FIGURE 1 is a top plan view of the above-referred to towing winch;

FIGURE 2 is a side elevational view of the winch shown in FIGURE 1;

FIGURE 3 is an enlarged sectional view of the spooling unit ,cross headtaken generally on the line 3-3 of FIGURE 1;

FIGURE 4 is a schematic rear elevational view of the winch of FIGURE 1;

FIGURE 5 is an enlarged sectional view of the spooling control unittaken on the line 55 of FIGURE 1;

FIGURE 6 is an enlarged fragmentary view of the spooling control unitpartly in section and partly in elevation looking in the direction ofthe arrows 66 of FIGURE 1;

FIGURES 7 and 8 are sectional views taken on the lines 7-7 and 8-8,respectively, of FIGURE 6;

FIGURE 9 is an enlarged sectional view of the planetary gear set ofFIGURE 6;

FIGURE 9A is a fragmentary sectional view taken on the line 9A-9A ofFIGURE 9;

FIGURE 10 is a diagram of the hydraulic systems for the windup drum andfor the spooling rams; and

FIGURE 11 is a schematic view illustrating the operation of the parts ofthe planetary gear set of FIGURES 6 and 9.

Detailed description of mechanical components of windup drum andspooling unit Referring to FIGURES l and 2, there is shown in somewhatsimplified form, a towing winch 10 having a hydraulically operatedwindup drum 12 and a hydraulically operated spooling unit 14 supportedby a common main frame. The towing winch 10 is assumed to be mountednear the aft end of a ship with the longitudinal midplane of the shippassing through the axis of the windup drum 12 at a right angle. Theframe consists essentially of two spaced apart, vertical framesubassemblies 16 with appropriate horizontal bracing members extendingbetween them. In the interest of simplicity of illustration the detailsof the framing is not shown, and all fixed parts which serve as supportsare identified with the same reference numeral. The windup drum 12 isprovided with an integral shaft 18, the ends of which are mounted inbearings 20 carried by the frame subassemblies 16. The spooling unit 14is carried by the frame subassemblies 16 in a position aft of the windupdrum 12 and above the axis thereof. Carried on the port side (the rightside as viewed in FIGURE 1) subassembly are two hydraulic motors 22 fordriving the windup drum 12 and a manually-operated winch control lever24 which is mechanically linked to the spool of a pilot valve 26 (FIGURE10). The pilot valve 26 is hydraulically connected to a main controlvalve 28 (FIGURE 10) which controls the direction of rotation of themotors 22. Also carried on the port side subassembly '16 is a mechanicalspooling control unit 30 for actuating a control valve 32 (FIGURE 10) inthe hydraulic drive of the spooling unit 14. The control unit 30receives one rotary input from the windup drum 12 through a connectionwhich includes an internal input shaft 34 (FIGURE 7) and another rotaryinput from the spooling unit 14 through a connection which includes anexternal input shaft 36.

The hydraulic motors 22 for the windup drum are drivingly connected, asby spur gears 38, to a horizontal transverse shaft which is disposedforward of the windup drum 12. The shaft 40 is journalled in the portside frame subassembly 16 and in a pedestal bearing 44 located outwardlyof the latter. The outer end of the shaft 40 carries a conventionalwinch head 46. The inner end of the shaft 40' connects through amanually operated jaw clutch 48 with the inner end of a drum drive shaftso that the winch head 46 may be operated independently of the windupdrum 12 when the clutch 48 is disengaged. The drum drive shaft 50 isjournalled in the other frame subassembly and carries a pinion whichmeshes with a large drive gear 54. The latter is coaxial with the windup drum 12 and is bolted to the starboard end thereof. The outer end ofthe drum drive shaft 50 carries a large brake drum 56 around which isfitted a steel brake band 58 lined with woven asbestos lining. The brakeband 58 is adjustably tightened on the brake drum 56, through levers,links and a large screw, by rotation of a handoperated wheel 62. Thebrake has sufficient power, when properly tightened, to prevent a largepredetermined pull, for example 140,000 pounds, on the first layer ofrope to overhaul the windup drum when the clutch 48 is disengaged. Thebrake will slip when the pull on the rope exceeds the predeterminedholding force.

The hydraulic pumps and piping for the motors 22 has been omitted fromFIGURES 1 and 2 in the interest of simplicity. This hydraulic system isillustrated schematically in FIGURE 10 and will be describedhereinafter.

The hydraulically operated spooling unit 14 includes two pairs ofopposed horizontal rams 64 supporting a cross head 66 which carries afair lead swivelblock 68. The cylinders 70 of the rams 64 are fixed tothe outboard sides of the frame subassemblies 16 in a location aft ofthe windup drum 12 and above the axis thereof. The pistons 72 extendthrough the frame subassemblies 16 into sockets on the cross head 66. Inoperation one set of cylinders 70 is pressurized while the other set isconnected to exhaust so that the cross head 66 may be moved parallel tothe axis of the windup drum 12 in either direction by whichever set ofpistons 72 is being extended.

As best seen in FIGURE 3, the fair lead swivel block 68 carries a mainsheave 76 and a secondary sheave 78 and is provided with a hollowcylindrical extension 80 through which the rope 82 passes. Thecylindrical extension 80 is swivelly mounted in a bore in the center ofthe spooling unit cross head by means of roller bearings 84 for 360 ofrotational movement about a fore and aft axis through the center of theextension 80. In operation, the swivel block 68 will assume the positionshown in FIGURES 1 and 2 when the rope 82 is being payed out or wound inalong the ships fore and aft center line, in which case the axis ofrotation of the sheaves 76 and 78 is parallel to the axis of rotation ofthe windup drum 12 and to the direction of movement of the cross head66. As the lead of the rope 82 changes, the swivel block 68 will rotateabout the axis defined by the roller bearings 84. At of lead the rope 82is parallel to the axis of the windup drum 12, and the swivel block 68will assume one of the dotted line posi tions illustrated in FIGURE 1 inwhich position the axes of the sheaves are normal to the windup drumaxis.

As seen in FIGURE 4, the lower end of the cross head 66 is fitted with abracket 86 to which is secured an endless wire rope 88. The wire rope 88is looped over a pair of spaced apart repeat back rope drums 90 and 92,each of which is journalled on one of the frame subassemblies 16 forfree rotation about a fore and aft axis. The wire rope 88 is wrappedaround the drum 92 to prevent slippage between the two. Linear movementof the cross head 66 under the action of one of the sets of pistons 72rotates the drums 90 and 92, and this rotary movement is transmitted toa shaft 94 which is coupled to the external rotary input shaft 36 of thespool control unit 30 through a universal joint 96.

Detailed description of spool control unit As previously indicated, thespool control unit 30 (FIGURES 5-9), which is mounted on the port sideframe subassembly 16, is a mechanical servo-mechanism for synchronizingthe movement of the spooling unit cross head 66 with rotation of thewindup drum 12. The ultimate output of the control unit 30 is in theform of movement of a lever which moves the spool of the control valve32 (FIGURE 10) for the spooling rams 64.

The control valve 32 is a four-way valve having a center position inwhich the rams 64 are hydraulically locked and two end positions inwhich the spooling unit cross head 66 is driven either to the left or tothe right.

The heart of the control unit is a planetary gear set (FIGURES 6, 9 and9A) which revolves a grooved barrel cam 117, the latter determining theposition of the directional control valve 32 (FIGURE 10) by means of avalve control lever 136 (FIGURE 5). The gear set 100 includes twocoaxial, spaced-apart sun gears 102 and 104 and two intermeshingplanetary pinions 106 and 108, one of which (106) meshes with the firstsun gear 102 and the other of which (108) meshes with the second sungear 104. The shafts of the pinions are rotatably mounted at 1060 and108a in spaced-apart plates which, together with a hollow cylindricalmember 107, form a planetary carrier 110 or spider. One sun gear 102 isfixed to a shaft 112 extending out of the gear set 100 and journalled ina bearing 114 within the control unit 30. The other sun gear 104 isfixed to an oppositely directed shaft 116 which is journalled in abearing 118. The shaft 112 is rotated by a mechanical drive connectedwith the windup drum 12 and provides a first rotary input to the gearset 100; the shaft 116 is rotated by movement of the spooling unit crosshead 66 and provides a second rotary input to the gear set 100.

The planetary carrier 110 carries a barrel cam 117 which is made up of ahollow member 119 and two end plates 120 secured together by bolts 121.The end plates 120 are keyed at 122 to oppositely directed stub shafts123 which project from the ends of the planetary carrier 110. Theexterior surface of the barrel cam 117 presents an axially facing camsurface 126 which is engaged by a roller 128 (FIGURE 8) carried out byone end of an arm 130. The other end of the arm 130 is keyed to arotatable stub shaft 132 (FIGURE 8) which is mounted in a pair ofspaced-part bushings 134. The control lever 136 for the spooling unitcontrol valve 32 is keyed to the stub shaft 132.

The overall operation of the gear set 100 is such that rotation of theplanetary carrier 110 is responsive to the rotary inputs to the sungears 102 and 104. Rotation of the carrier 110 rotates the barrel cam117 and this moves the valve control lever 136 so as to start themovement or stop the movement or to reverse the directions of movementof the spooling rams 64 at the proper times.

The rotary input to the sun gear 104 is directly proportional to thelinear movement of the spooling unit cross head 66 and is provided bythe extenal shaft 36 which is driven by the shaft 94 from the repeatback rope drum 92. As best seen in FIGURE 6, the external shaft 36 iskeyed at 139 to the planetary carrier shaft 116 just outside the controlunit 30.

The rotary input to the sun gear 102 is obtained from the windup drum 12through a mechanical connection which includes a diamond lead screw 140.The mechanical connection begins with the previously mentioned internalinput shaft 34 which, as seen in FIGURE 7, is coaxial with the windupdrum shaft 18 and connected thereto by a sleeve 141 which is bolted tothe drum shaft 18 at 142. The sleeve 141 is keyed to a miter gear 143which in turn is keyed to the shaft 34, and the assembly of these partsis rotatably mounted in bearings 144. The miter gear 143 meshes withanother miter gear 146 which is keyed to a shaft 148 (FIGURE 5). Thelatter shaft is journalled in bearings 150 and carries a pinion 152 anda hand wheel 154. The hand wheel 154 is accessible for manual rotationby removal of a cover plate 156 which forms part of the casing of thecontrol unit 30. The pinion 152 meshes with a spur gear 158 which iskeyed to one end of the diamond lead screw 140, the latter beingjournalled in bearings 160.

Continuous rotation of the lead screw 140 in either direction isconverted to rotary reciprocating movement of the sun gear 102 of theplanetary set 100 by means of 6 a swivel pawl cross head 162, a rack164',- spur gear 166, shaft 168 and helical gears 170 and 172, thelatter being keyed to the sun gear shaft 112 as seen in FIGURE 6. Theswivel pawl cross head 162 (FIGURE 5), which includes a swivel nut 174,cooperates with the lead screw 140 and is moved linearly by rotation ofthe latter. Rotation of the pawl 162 is prevented by two fixed guiderods 176 on which the pawl 162 slides. The relationship of the pawl 162,lead screw 140 and the spooling unit cross head 66 is such that the pawl162 arrives at its reversal point slightly before the spooling crosshead 66 arrives at its reversal point. The rack 164, which extendsparallel to the lead screw 140, is fixed to the pawl 162 and is therebymoved longitudinally of itself inside the control unit 30 duringrotation of the lead screw 140. The extrernities of the rack 164 areenclosed by covers 178 and 180 which project from the main portion ofthecontrol unit 30, as seen in FIGURE 6.

The teeth 182 of the rack 164 mesh with the spur gear 166 which is keyedto the shaft 168. Rotation of the latter within its supporting bearings184 rotates the helical gear 17 0 which in turn rotates the helical gear172. The helical gear 172 is keyed to the sun gear shaft 112, aspreviously described.

FIGURE 10 shows the hydraulic circuits for the windup drum 12 and forthe spooling rams 64.

The motors 22 for the windup drum 12 are of a commercially available lowspeed, high constant torque type having fixed displacement and are fullyreversible with identical torque being produced in either direction ofrotation. Pressure oil for the motors is supplied by four independentvane-type hydraulic pumps which are located remote from the motors 22.Two compensator pumps 186 are driven by electric motors, for example 25HP motors producing oil at up to 750 p.s.i. The other two pumps 188 aredriven by diesel-powered generators, for example, 75 kw. producing 2100p.s.i. oil. Pressure oil from the pumps 188 is made available directlyto the main motor control valve 28 through lines 190, 192 and 194.Exhaust oil from the valve 28 passes through a line 196.

Pressure oil from the pumps 186 passes to the motor control valve 28 byway of a selector valve 198 which is adapted to direct oil from eitherone of the pumps 186 to a line 199 which connects with the circuit 190,192, 194. The oil from the other pump 186 is directed to a line 200 foruse by the spooling rams 64 and by the ships steering mechanism.

The hydraulic circuit between the main control valve 28 and the motors22 includes lines 202 and 204 and a relief valve 206, the latter beingarranged with appropriate check valves to pass oil to an exhaust line208.

As previously indicated, the spool of the main control valve 28 is movedhydraulically by pressure oil received from the pilot valve 26. Acompensator vane pump 210 supplies pilot pressure oil to the pilot valve26 through a line 212 and supplies supercharging oil to the motors 22through a line 214. The pressure oil from the line 212 is passed to theactuators of the pilot valve 26 through either of lines 216 or 218 andthen to exhaust through a line 220.

Pressure oil from either of the pumps 186 is made available to the ramcontrol valve 32 through the selector valve 198, the line 200 and a line222. Return oil passes through a return line 224 which connects with theexhaust line 220. The valve 32 passes oil to and from the rams 64through a circuit which includes lines 226 and 228. Relief valves 230and 232, together with appropriate check valves are provided between thelines 226 and 228 for exhausting oil to the exhaust line 208. The spoolof the valve 32, when centered, blocks the flow of oil to or from thelines 226 and 228 and hydraulieally locks the rams 64. However, a bypassvalve 234 is provided between these lines so that, when the valve 234 7is open, one set of rams 64 may extend freely while the other setretracts.

Operation As indicated previously, the hydraulic motors 22 which drivethe windup drum 12 are controlled manually with the lever 24 which ismechanically linked to the spool of the pilot valve 26. In the neutralposition of the lever 24 the spools of both the pilot valve 26 and themain motor control valve 28 are centered. The spool of pilot valve 26blocks the flow of pilot pressure oil from the line 212 and connects thelines 216 and 218 to the exhaust line 220. The pilot pump 210 continuesto operate but its discharge is reduced by the compensator as thepressure increases until no oil is discharged at 150 psi. The spool ofthe main control valve 28 passes pressure oil from the line 194 directlyto the exhaust line 196. The spool of the main valve 28 also blocks theflow of oil in either direction in the lines 202 and 204, thushydraulically locking the motors 22 to prevent overhaul of the drum 12.When moved to a down position the lever 24 moves the spool of the pilotvalve 26 to pass pressure oil to the actuator of the main control valve28. This moves the spool of the latter to a first open position in whichpressure oil from the pumps is passed to the motors 22 in a direction tohaul in rope. In the up position the lever 24 moves the main valve spoolto the second open position which permits the pressure oil to rotate themotors in the direction to pay out rope.

The relief valve 206 opens when the pressure in the motor system reachesa predetermined high pressure for example 21.00 p.s.i. and permits thepressure oil to by-pass to the lines 202 or 204. This relief valve 206prevents overloading the motors 22 and pumps and permit rope to pay outfrom the windup drum when the external pull on the rope develops apressure in the system which exceeds the relief valve pressure setting.

The motors may be driven by different combinations of the pumps 186 and188 to handle different loads and speeds. For a pull of 10,000 lbs. at70 f.p.m. on the first layer of rope on the windup drum 12, both pumps188 and one of the pumps 186 are employed. In this case the line ispressurized by oil passing from the pumps 188 through the lines 190 and192 and by oil passing from the selector valve 198 through the line 199.For a pull of 25,000 lbs. at 45 f.p.m. on the first layer of rope on thedrum 12, one of the pumps 188 and one of the pumps 186 are employed. Fora pull of 50,000 lbs. 'at 24 f.p.m. or of 100,- 000 lbs. at 23 f.p.m.one of the pumps 188 alone is employed. Neither of the pumps 186 willdischarge oil when the load on the windup drum becomes high, because inthis event the pressure in the line 194 exceeds the pressure setting ofthe compensators tor the pumps 186.

The spooling rams 64 are operated by pressure oil obtained from the line222 under the control of the spooling control valve 32 which is actuatedby the spooling control unit 30. The control valve 32 has a centerposition in'which oil fiows neither to or from the rams 64 with theresult that the latter are hydraulically locked against extension orretraction. In one end position the valve 32 directs pressure oil to oneset of rams 64 through one of the lines 226, 228 while exhausting theother set through the line 224. In the other end position the valve 32reverses the flow of oil so as to reverse the movement of the rams 64.The relief valves 230 and 232 open at a predetermined high internalpressure, for example 1500 psi, and permit the pressure oil to by-passto the opposite side of the system. During operation of the ra-ms 64 thevalves 230 and 232 permit the spooling unit 14 to be moved transverselyof the ship in either direction by the pull of the rope sheave 76 whenthis load develops pressure in the spooling rams 64 greater than therelief valve setting. The spooling unit piping is also provided with thebypass valve 234 which, when opened, permits free movement of thespooling unit 14 in either direction by external forces on the ropesheave 76. The connection of the pressure line 222 to the line 200permits the rams 64 to be operated regardless of whether the line 194 tothe motor control valve 28 is being pressurized.

The spooling control valve 32 is operated solely by the spooling controlunit 30 through the cam-operated lever 130 (FIGURE 8) and the linkage134, 136 interconnecting the valve 32 and the lever 130. The controlunit 30 operates as a servo unit in that it rapidly adjusts the positionof the control valve 32 in response to inputs which are proportional tomovements of certain parts of the winch. The primary overall function ofthe control unit is, of course, to reverse the direction of movement ofthe spooling rams 64 in proper synchronization with rotation of thewindup drum 12. This is accomplished, in part, with the diamond leadscrew 140 and associated pawl 162, the lead screw 140 being rotated by adirect mechanical drive from the windup drum 12. The relationshipbetween the lead screw 140' and the pawl 162 is such that the pawl 162reverses its direction of movement just before the spooling unit crosshead 66 reaches the point at which it should reverse. However, thestopping and reversal of the pawl 162 is not converted directly intomovement of the valve control lever 130 to its reverse position. Rather,the stopping of the pawl 162 is employed to initiate a closing signalfor transmittal to the valve 32, and the beginning of the subsequentreverse movement of the pawl 162 is employed to initiate avalve-reversing signal. In order to accomplish this sequence the controlunit 30 continuously receives a second mechanical input which isdirectly proportional to the actual movement of the spooling unit 14.The latter input is compared with the pawl movement by the planetarygear set in such a manner that the movement of the spooling unit 14,after the pawl 162 stops, efifects movement of the cam 117 and controllever 130 to the closed position. Thus, the spooling unit 14 in effectproduces its own control signal. The planetary gear set 100 alsocompares the pawl movement with the second input in such a manner thatthe beginning of subsequent movement of the pawl 162 in its reversedirection effects movement of the cam 117 and valve lever 130 to theappropriate open position.

The effect of the above-outlined sequence of steps is to reverse thedirection of the spooling unit 14 with a minimum of stress within thehydraulic system. The spooling unit 14 is of necessity a heavy piece ofequipment. The inertia of the equipment plus the external forces actingon the sheave 76 through the rope 82 would on occasion create very highpressures in the hydraulic system if the control valve 32 were moveddirectly from one open position to a reverse open position. The controlunit 30, however, assures that the valve 32 will first move to a closedposition before reversing and assures that the necessary synchronismwill be maintained between rotation of the drum 12 and reversal of thespooling unit 14.

The actual movement of the parts of the planetary gear set 100 and theresulting movement of the cam 117 before, during and after reversal ofthe spooling unit 14 is illustrated schematically in FIGURE 11(a)through FIGURE 11(i). The gear set 100 is shown as if viewed from theright in FIGURE 9, and in the interest of simplicity the planetarycarrier is shown fragmentarily as an arcuate line. The cam arrangement117, 119, 120, 126 is shown as a single projection on the outside of thecarrier 110. One half of each sun gear 102 and 104 has been broken awayso that both gears appear in the views.

The arrows designate the direction of rotation of the various parts.Where no arrow appears that part is stationary.

FIGURE 11(a) illustrates the operation of the parts during a routinepass of the spooling unit 14 along the length of the windup drum 12.During this time the windup drum 12 is rotating in one direction or theother depending on whether rope 82 is being payed out or wound in. Ineither case the continuous rotation of the drum 12 is transmitted to thediamond lead screw 140 through the connection formed by parts 34, 143,146, 148, 152 and 158. Assuming that the pawl 162 is in a positionintermediate the ends of the lead screw 140, the pawl 162 will be movedlinearly along its support rods 176 by the action of the screw 140.Linear movement of the pawl 162 moves the rack 164 with the result thatrotary motion is imparted to the sun gear 102 by parts 166, 168, 170,172 and 112. At the same time rotary motion in the opposite direction isbeing imparted to the other sun gear 104 by movement of the spoolingunit 14, cable 88, repeat back drums 90 and 92 and shafting 94, 36 and116. At this stage of the description it is assumed that the controlvalve 32 is open to one of its two open positions this position beingindicated as No. l, and that one set of spooling pistons 72 is pushingthe spooling unit 14 along the length of the windup drum 12.

Thus, during traversal of the spooling unit 14 there are two rotaryinputs to the planetary gear set 100. As seen in FIGURE ll(a), the sungear 102 is being driven clockwise, and the sun gear 104 is being drivencounterclockwise. Each of the planetary gears 106 and 108 is also beingrotated about its own axis by its respective sun gear. The gear set 100is so designed that the rotary inputs cancel each other with the resultthat the planetary carrier 110 and cam 117 are stationary duringtraversing movement of the spooling unit 14. Accordingly, the cam 117remains in the No. 1 position until the pawl 162 stops at one end of thelead screw 140, as discussed in the next paragraph.

FIGURE ll(b) illustrates the movement of the parts which occurs when thepawl 162 reaches the end of the lead screw 140 and stops momentarilybefore reversing. Since the pawl 162 indirectly drives the sun gear 102,the latter stops when the pawl 162 stops. However, the sun gear 104continues to rotate counterclockwise as before, because the spoolingunit 14 is still moving toward one end of its path of travel. That is,the repeat back drums 90 and 92 continue to rotate in the same directionas before with the result that the rotary input to the sun gear 104 doesnot change. Since the sun gear 102 is stationary and the sun gear 104 isrotating, the carrier 110 will be rotated counterclockwise through theaction of the planetary gears 106 and 108. The result is that the cam117 moves toward a closed position C. In this position of the cam 117the spool of the control valve 32 is in a center position in which nooil flows to or from either set of rams 64. Accordingly, in thisposition of the cam 102 the pistons 72 are stationary and hydraulicallylocked against movement.

FIGURE ll(c) illustrates the parts immediately after the cam 117 reachesthe closed position referred to above. Since the pistons 72 havestopped, the spooling unit 14 and repeat drums 90 and 92 have stopped.This stops ro tation of the sun gear 104, and since there is now norotary input to the gear set 100, the cam 117 stops.

Referring to FIGURE ll(d), the pawl 162 now begins to move in theopposite direction because the lead screw 140 and windup drum 12 havecontinued to rotate without interruption. This reverse movement of thepawl 162 drives the sun gear 102 in a counterclockwise direction. Sincethe sun gear 104 is stationary and locked, counterclockwise rotation ofthe sun gear 102 causes the carrier 110 and the cam 117 to move again ina counterclockwise direction. This moves the cam 117 from the closedposition toward an opposite open position, No. 2, in which the spool inthe control valve 32 directs pressure oil to the opposite set of pistons72, thus pushing the spooling unit 14 in the opposite direction.

As soon as there is movement of the spooling unit 14, the repeat backdrum 92 imposes a rotary input on the sun gear 104, this time in aclockwise direction as shown in FIGURE ll(e). This counteracts therotary input to the sun gear 102 so that the carrier 110 and cam 117become stationary at the No. 2 open position.

FIGURE 11( is analogous to FIGURE ll(b) and represents the stopping andlocking of the sun gear 102 as the pawl 162 again reaches an end of thelead screw 140. The clockwise input to the sun gear 104 continues, andthis causes the carrier 110 and cam 117 to move clockwise toward theclosed position.

FIGURE ll(g) is identical to FIGURE 11(0) and represents the stationaryposition of the carrier 110 and cam 117 after the input to the sun gear104 stops as a result of closing of the valve 32.

FIGURE ll(h) is analogous to FIGURE ll(d) in showing rotation of the sungear 102 as the pawl 162 again starts to move in its original direction.Since the valve 32 is still closed, the sun gear 104 is locked. Thecarrier 110 and cam 117 therefore begin to rotate clockwise toward theNo. 1 open position.

In FIGURE ll(i) the cam 117 has arrived at the No. 1 open position withthe result that the valve 32 has opened, the spooling unit 14 is beingmoved and the repeat back drum 92 is driving the sun gear 104 in acounterclockwise direction. Again, the inputs to the gear set canceleach other so that the cam 117 is stationary. Accordingly, FIGURE ll(i)is identical with FIGURE ll(a).

If the operator of the winch stops the wind-up drum 12 by closing thepilot valve 26 with the manually operated lever 24, the diamond leadscrew 140 stops and the rotary input to the sun gear 102 stops. Sinceoil flow to one set of spooling pistons 72 continues, the rotary inputto the sun gear 104 continues. However, from FIGURES ll(b) or (f) itwill be apparent that the rotation of the sun gear 104 will immediatelycause rotation of the carrier and cam 117 to the closed position, so asto close the valve 32 and shut down the spooling drive. Upon theoperators starting the winding drum 12 the sun gear 102 will begin torotate and will move the carrier 110 and cam 117 to the appropriate openposition, as illustrated in FIGURE ll(a) or (e).

Adjustment of the spooling control unit 30 so that it operates asdescribed above is made by manually rotating the wheel 154 shown inFIGURE 5, after removing the cover 156 and after disconnecting theuniversal joint 96 shown in FIGURE 6. The wheel 154 which is fixed tothe shaft 148 is first moved slightly to the left as viewed in FIGURE 5so as to disconnect the gears 143 and 146. Next, the wheel is rotated torotate the lead screw and move the pawl 162 to the end of its travel. Ifthe spooling unit cross head 14 is at the port side of the winch, thepawl should be moved to the right as viewed in FIGURE 5. If the crosshead 14 is at the starboard side of the winch, the pawl 162 should bemoved to the left. The moving of the pawl 162, as described in theprevious sentences, centers the spool of the valve 32 by the action ofthe cam 117 and lever 136. Then the wheel 154 is pushed to the right toreengage the gears 143 and 146, and the cover 156 is replaced. Furtheradjustments of the spooling control unit 30 can be made, if required, bydisconnecting the universal joint 96 and rotating the input shaft 36 byhand until the spool of the valve 32 has been centered by the cam 102and lever 13-6. Finally, the universal joint 96 is re-connected whileholding the input shaft stationary.

While preferred embodiments of the present invention have beendescribed, further modifications may be made without departing from thescope of the invention. Therefore, it is to be understood that thedetails set forth or shown in the drawings are to be interpreted in anillustrative, and not in a limiting sense, except as they appear in theappended claims.

What is claimed is:

1. A control device for a line spooling unit of the kind employed inconjunction with a power driven windup drum and having a line guidingmeans and a drive means for reciprocating the line guiding means along apath between first and second limits corresponding to that length of thedrum adapted for carrying the line whereby the line may be spooled on oroff the' drum, said control device comprising: a movable output memberfor controlling the drive means for the line guiding means, said outputmember having at least one drive position and a stop position; firsttransmission means adapted to be driven at a speed proportional to thespeed of rotation of the windup drum, said first transmission meanshaving means for converting continuous rotation of the windup drum intouniform reciprocating movement of a first member; second transmissionmeans adapted to be driven at a speed proportional to the speed of theline guiding means along its path and in a direction corresponding tothe direction of movement of the line guiding means, said secondtransmission means having means for converting movement of the lineguiding means into reciprocating movement of a second member; and thirdtransmission means interconnecting said first and second members withsaid movable output member for moving said output member from a driveposition to its stop position and then to a drive position upon eacharrival of the line guiding means at one of its limits,

2. Apparatus as in claim 1 wherein said first transmission meansincludes a two-way lead screw adapted to be rotated at a speedproportional to the speed of rotation of the windup drum, a pawl mountedon said lead screw and linearly reciprocated by continuous rotation ofsaid lead screw and connecting means for converting reciprocating linearmovement of said pawl into reciprocating rotary movement of said firstmember and wherein the movement of said second member of said secondtransmission means is rotary and reciprocating.

3. Apparatus as in claim 2 wherein said third transmission meansincludes a planetary differential gear set having first and second sungears, a pair of intermeshing planetary gears and a planetary carrier,said first sun gear being drivingly connected to said first member ofsaid first transmission means, said second sun gear being drivinglyconnected to said second member of said second transmission means andsaid planetary carrier being drivingly connected to said output member,said planetary gears being rotatably mounted in said carrier, one ofsaid p'anetary gears being in meshing engagement with said first sungear and the other planetary gear being in meshing engagement with saidsecond sun gear.

4. In a machine having a rotatable windup drum and a spooling devicewhich includes line guiding means and drive means for traversing saidline guiding means, an improved control device for said drive meanscomprising: an output member having at least one drive position and astop position; means responsive to a predetermined amount of rotation ofthe windup drum and simultaneously responsive to continued movement ofthe line guiding means to move said output member from a drive positionto said stop position; means responsive to stoppage of the line guidingmeans to hold said output member in said top position; means responsiveto further rtation of the windup drum to move said output member to adrive position; and means responsive to movement of the line guidingmeans and simultaneously responsive to continued rotation of the windupdrum to hold said output member in said last-named drive position.

5. A power winch construction having a power-driven windup drum and aline spooling device disposed adjacent said windup drum, said spoolingdevice comprising: line guiding means disposed adjacent said windup forguiding a line between a remote point and said drum; first and secondhydraulic cylinder-and-piston units disposed on opposite sides of saidline guiding means, each of said units having an extensible andcontractable free end engaging an opposite side of said line guidingmeans for moving the same between two fixed limits along a straightlinepath parallel to the axis of said windup drum in a first direction uponsimultaneous extension of said first unit and retraction of said secondunit and in a second direction upon simultaneous extension of saidsecond and retraction of said second unit, said line guiding meansincluding a cross head engaged by said free ends of said piston andcylinder units and a swivel block, said swivel block including a hollowcylindrical extension extending transversely to the axis of said windupdrum and swivelly mounted in a complementary passage through said cross168d, said line guiding means further including a linereceiving sheavejournalled for rotation about its own axis on said swivel block on theopposite side of said hollow extension from said windup drum; and fluidpressure supply means for said piston-andcylinder units including valvemeans for delivering fluid under pressure to either of said units whileexhausting fluid pressure from the other of said units, said fluidpressure supply and control means includes a relief valve operable toexhaust fluid pressure from the piston-and-cylinder units uponoccurrence of predetermined high. fluid pressure whereby said lineguiding means may be moved against the action of a piston-and-cylinderunit by the pull of the line on said line guiding means when the pull issuflicient to develop pressure in excess of said predetermined highpressure.

6. A machine as in claim 4 wherein said drive means includes a linearhydraulic motor and a valve for controlling the fiow pressure fluid toand from said motor and wherein said output member of said controldevice is operably associated with said valve.

7. Apparatus as in claim 5 wherein said fluid pressure supply andcontrol means further includes a by-pass valve for exhausting fluidpressure from both said pistonand-cylinder units whereby said lineguiding means may be moved freely along said elongated support in eitherdirection by external forces on said guiding means.

8. Apparatus as in claim 5 wherein said valve means has a closedposition in which no pressure fluid flows to said cylinder-and-pistonunits and two opposite open positions, said control unit beingcontinuously and simultaneously responsive to rotation of said windupdrum and to movement of said line guiding means to move said valve fromone of its open positions to its closed position just before saidguiding means reaches one of its limits and to then move said valve toits opposite open position so as to reverse the flow of fluid pressureto said cylinderand-piston units.

References Cited UNITED STATES PATENTS 2,320,554 6/1943 Barrett 242-1582,391,290 12/1945 Berger 254190 2,404,368 7/1946 Esch 242-458 3,168,2612/1965 Hainer 242-158 3,174,726 3/1965 Atkinson M 254l FOREIGN PATENTS1,051,474 2/1959 Germany.

EVON C. BLUNK, Primary Examiner.

H. C. HORNSBY, Assistant Examiner.

